US7997242B2 - Spring retainer and spring system - Google Patents

Spring retainer and spring system Download PDF

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Publication number
US7997242B2
US7997242B2 US12/227,345 US22734507A US7997242B2 US 7997242 B2 US7997242 B2 US 7997242B2 US 22734507 A US22734507 A US 22734507A US 7997242 B2 US7997242 B2 US 7997242B2
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US
United States
Prior art keywords
spring
retainer
plate
set forth
valve
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Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Fee Related, expires
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US12/227,345
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English (en)
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US20090235882A1 (en
Inventor
Noritoshi Takamura
Hironobu Imaizumi
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NHK Spring Co Ltd
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NHK Spring Co Ltd
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Filing date
Publication date
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Assigned to NHK SPRING CO., LTD. reassignment NHK SPRING CO., LTD. ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: IMAIZUMI, HIRONOBU, TAKAMURA, NORITOSHI
Publication of US20090235882A1 publication Critical patent/US20090235882A1/en
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F3/00—Spring units consisting of several springs, e.g. for obtaining a desired spring characteristic
    • F16F3/02—Spring units consisting of several springs, e.g. for obtaining a desired spring characteristic with springs made of steel or of other material having low internal friction
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L3/00—Lift-valve, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces; Parts or accessories thereof
    • F01L3/10—Connecting springs to valve members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F1/00—Springs
    • F16F1/02—Springs made of steel or other material having low internal friction; Wound, torsion, leaf, cup, ring or the like springs, the material of the spring not being relevant
    • F16F1/04—Wound springs
    • F16F1/12—Attachments or mountings
    • F16F1/126—Attachments or mountings comprising an element between the end coil of the spring and the support proper, e.g. an elastomeric annulus
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T74/00—Machine element or mechanism
    • Y10T74/18—Mechanical movements
    • Y10T74/1856—Reciprocating or oscillating to intermittent unidirectional motion

Definitions

  • the present invention relates to a spring retainer used to support a coil spring such as a valve spring and to a spring system incorporating a coil spring.
  • Patent Document 1 shows a configuration that supports a valve spring with double springs.
  • This technique relates to a valve rotator for an internal combustion engine with a rotator body having a disc spring and a coil spring which is a circumferential garter spring.
  • the garter spring is received in a groove of the rotator body and is in contact with a top surface of the disk spring.
  • a bottom surface of the disk spring contacts and supports the valve spring.
  • the disk spring When the disk spring upwardly deflects, it pushes and inclines the garter spring in a circumferential direction. According to the inclination, the rotator body turns around a valve axis to forcibly turn the valve.
  • the disk spring and garter spring must have lower spring constants than the valve spring. This results in lowering an overall spring constant to limit reductions of the set height and mass of the valve spring.
  • Patent Document 1 Japanese Unexamined Patent Application Publication No. H08-180308
  • a problem to be solved is the limit on reductions of the set height and mass of a coil spring.
  • the present invention is most characterized by a plate-like spring part having an inner circumferential part supported by a retainer body and resiliently supporting an end of the coil spring, and a spring constant of the plate-like spring part is higher than a spring constant of the coil spring.
  • a spring retainer has the plate-like spring part having an inner circumferential part supported by the retainer body and resiliently supporting an end of the coil spring, and the spring constant of the plate-like spring part being higher than the spring constant of the coil spring. After the coil spring is compressed, the plate-like spring part deflects. Due to the deflection of the plate-like spring part, a set height and a compressed height can be suppressed and a mass can be reduced.
  • FIG. 1 is a sectional view showing an essential part of a spring system with a valve spring in a set state according to Embodiment 1 of the present invention
  • FIG. 2 is a plan view showing the spring system with the valve spring in the set state according to Embodiment 1 of the present invention
  • FIG. 3 is a sectional view showing an essential part of a spring system with a valve spring in a set state according to comparative example
  • FIG. 4 is a graph showing a load-deflection characteristic of a plate-like spring part according to Embodiment 1 of the present invention.
  • FIG. 5 is a graph showing load-deflection characteristics with the valve springs in the set states according to Embodiment 1 of the present invention.
  • FIG. 6 is a table comparing set heights of valve springs and the like.
  • FIG. 7 is a table comparing dynamic stress
  • FIG. 8 is a table comparing mass
  • FIG. 9 is a sectional view showing a spring retainer according to Embodiment 2 of the present invention.
  • FIG. 10 is a plan view showing the spring retainer according to Embodiment 2 of the present invention.
  • FIG. 11 is a sectional view showing a spring retainer according to Embodiment 3 of the present invention.
  • FIG. 12 is a plan view showing the spring retainer according to Embodiment 3 of the present invention.
  • FIG. 13 is a sectional view showing a spring retainer according to Embodiment 4 of the present invention.
  • FIG. 14 is a plan view showing the spring retainer according to Embodiment 4 of the present invention.
  • FIG. 15 is a side view showing a spring retainer according to Embodiment 5 of the present invention.
  • FIG. 16 is a plan view showing the spring retainer according to Embodiment 5 of the present invention.
  • An object of further reducing the set height and mass of a coil spring is achieved by the plate-like spring part whose spring constant is larger than that of the coil spring.
  • FIG. 1 is a sectional view showing an essential part of a spring system in which a valve spring is set with the use of a spring retainer according to Embodiment 1 of the present invention and FIG. 2 is a plan view showing the same.
  • the spring retainer 1 has a retainer body 3 and a circumferential plate-like spring part 5 .
  • the retainer body 3 is made of titanium alloy, aluminum alloy, or the like. An inner circumference of the retainer body 3 is provided with a tapered hole 6 and an outer circumference thereof is provided with a fitting part 7 and a collar 9 that are formed in steps. The retainer body 3 is attached through a cotter 13 to a stem end 11 of a valve.
  • the plate-like spring part 5 is a disk spring that resiliently supports an end 17 of a valve spring 15 which is a coil spring.
  • the plate-like spring part 5 has an inner circumferential part 19 and an outer circumferential part 21 that is inclined toward the valve spring 15 relative to the inner circumferential part 19 .
  • the inner circumferential part 19 of the plate-like spring part 5 is press-fitted and fixed to the fitting part 7 of the retainer body 3 and the outer circumferential part 21 thereof radially outwardly protrudes from the collar 9 and is supported so that it can be inverted in a valve stem axis direction.
  • Spring constants are so set that a spring load of the plate-like spring part 5 is higher than a spring load of the valve spring 15 .
  • the spring constant K 1 of the plate-like spring part 5 is set to be higher than the spring constant K 2 of the valve spring 15 , i.e., K 1 >K 2 .
  • the plate-like spring part 5 slightly deflects according to a load and supports the valve spring 15 .
  • the plate-like spring part 5 starts to further deflect, to provide a two-step load characteristic.
  • the plate-like spring part 5 is able to invert due to a load from the valve spring 15 , thereby realizing a wide deflecting range.
  • FIG. 3 is a sectional view showing an essential part of a spring system in which a valve spring is set with the use of a spring retainer according to a comparative example. Structural parts corresponding to those of FIG. 1 are explained with like reference marks plus A.
  • the spring retainer 1 A is made of titanium alloy, aluminum alloy, or the like.
  • a collar 9 A directly supports an end 17 A of a valve spring 15 A.
  • the valve spring 15 A provides a two-step load characteristic with, for example, a closely-coiled part.
  • a load of the valve spring 15 A is applied to an outer circumferential edge of the collar 9 A.
  • the embodiment of the present invention of FIG. 1 applies a load of the valve spring 15 through the plate-like spring part 5 to a base of the collar 9 .
  • the collars 9 and 9 A have different points where bending moment acts. Due to this, the height H 1 of the retainer body 3 of the embodiment shown in FIG. 1 can be reduced lower than the height H 2 of the spring retainer 1 A of the comparative example shown in FIG. 3 .
  • the embodiment therefore, can reduce the weight and height of the retainer.
  • FIG. 4 is a graph showing a load-deflection characteristic of the plate-like spring part.
  • an abscissa indicates displacement in mm and an ordinate indicates load in N.
  • the plate-like spring part 5 has dimensions of, for example, 23 mm in outer diameter, 17 mm in inner diameter, and 0.6 mm in plate thickness.
  • a valve set load (set load) of 180 N a deflection of 0.14 mm occurs as shown in FIG. 4 .
  • a valve opening load of 445 N With respect to a valve opening load of 445 N, a slight deflection of 0.45 mm occurs.
  • valve spring 15 With the plate-like spring part 5 , the valve spring 15 is set as shown in FIG. 1 .
  • the two-step load characteristic is realized without a closely-coiled part with the valve spring 15 having equal pitches.
  • FIG. 5 is a graph showing load-deflection characteristics each with a valve spring being in a set state. Namely, there are shown a characteristic (continuous line in FIG. 5 ) representing the spring system employing the spring retainer 1 of the embodiment of the present invention and the valve spring 15 and a characteristic (dotted line in FIG. 5 ) representing the configuration of FIG. 3 of the comparative example employing the valve spring having a closely-coiled part.
  • the plate-like spring part 5 involves the deflection thereof and reduces the deflection of the valve spring compared with the comparative example when a set load of 180 N or a valve opening load of 445 N is applied.
  • the plate-like spring part 5 When the valve spring 15 is brought into a compressed state, the plate-like spring part 5 generates a large load with a small deflection, to thereby provide the two-step load characteristic.
  • FIG. 6 is a table showing comparison of the set heights and the like of valve springs among standard springs and springs with the retainers of the embodiment.
  • ( 1 ) and ( 2 ) relate to the standard springs and ( 3 ) to ( 5 ) relate to the springs with the retainers of the embodiment.
  • ( 1 ) employs a valve spring having 3.2 mm in wire diameter, 17.0 mm in coil inner diameter, and 1.70 in the number of damper turns.
  • ( 2 ) employs a valve spring having 3.2 mm in wire diameter, 17.0 mm in coil inner diameter, and equal pitches with 0 in the number of damper turns.
  • ( 3 ) employs the embodiment of the present invention having 3.2 mm in wire diameter, 17.0 mm in coil inner diameter, and 0 in the number of damper turns.
  • ( 4 ) employs the embodiment of the present invention having 3.1 mm in wire diameter, 17.0 mm in coil inner diameter, and 0 in the number of damper turns.
  • ( 5 ) employs a valve spring having 3.2 mm in wire diameter, 17.0 mm in coil inner diameter, and 1.70 in the number of damper turns.
  • the height of the valve spring 15 of each of ( 3 ) and ( 4 ) according to the embodiment is lower than that of the equal-pitch standard valve spring ( 2 ) under a set load of 180 N and a valve opening load of 445 N. Namely, each of ( 3 ) and ( 4 ) can reduce the height. Similar comparison shows that each can reduce the height of a compressed state.
  • the height of the valve spring under a set load of 180 N and a valve opening load of 445 N is lower than the height of the valve spring ( 1 ) having a closely-coiled part. Namely, it can reduce the height. Similar comparison shows that it can reduce the height of a compressed state.
  • FIG. 7 is a table showing comparison of dynamic stress.
  • ( 1 ), ( 3 ), ( 4 ), and ( 5 ) of FIG. 7 correspond to ( 1 ), ( 3 ), ( 4 ), and ( 5 ) of FIG. 6 .
  • FIG. 8 is a table showing comparison of mass. ( 1 ), ( 3 ), ( 4 ), and ( 5 ) of FIG. 8 correspond to ( 1 ), ( 3 ), ( 4 ), and ( 5 ) of FIG. 6 .
  • the valve spring 15 with the spring retainer 1 may increase the mass thereof by the mass of the plate-like spring part 5 .
  • spring load produced by the plate-like spring part 5 helps to reduce the height and mass of the valve spring 15 .
  • ( 3 ), ( 4 ), and ( 5 ) of the embodiment each can realize lightness compared with the example ( 1 ) having a closely-coiled part.
  • Embodiment 1 of the present invention employs the retainer body 3 attached to the stem end 11 of a valve and the circumferential plate-like spring part 5 having the inner circumferential part 19 supported by the retainer body 3 and resiliently supporting the end 17 of the valve spring 15 .
  • the spring constant K 1 of the plate-like spring part 5 is higher than the spring constant K 2 of the valve spring 15 , so that the plate-like spring part 5 deflects after the valve spring 15 is compressed, to provide the two-step load characteristic.
  • the plate-like spring part 5 is supported so that it can invert. This increases a deflection stroke of the plate-like spring part 5 , to further reduce the height and mass of the valve spring 15 and those of an entire spring system.
  • the spring retainer 1 A of FIG. 3 supporting a valve spring having a closely-coiled part may provide the two-step load characteristic to effectively suppress a surge. This, however, puts a limit on an increase in a spring constant for a valve opening action, thereby limiting the surge suppressing effect.
  • the plate-like spring part 5 deflects after the valve spring 15 is compressed, to provide the two-step load characteristic. This improves a spring load produced after the valve spring 15 is compressed, thereby effectively suppressing a surge.
  • valve spring 15 has a closely-coiled part, it will provide a damping effect achieved when the closely-coiled part is compressed, as well as a damping effect achieved when the spring is entirely compressed. This configuration further improves the dynamic stress reducing effect.
  • FIGS. 9 and 10 relate to Embodiment 2 of the present invention, in which FIG. 9 is a sectional view showing a spring retainer and FIG. 10 is a plan view showing the same.
  • the spring retainer 1 B supports a plurality of plate-like spring parts 5 B that are laid one on another.
  • This embodiment can set a load by selecting the number of the plate-like spring parts.
  • FIGS. 11 and 12 relate to Embodiment 3 of the present invention, in which FIG. 11 is a sectional view showing a spring retainer and FIG. 12 is a plan view showing the same.
  • the spring retainer 1 C employs a plate-like spring part 5 C that is provided with inner and outer circumferential parts 19 and 21 between which there is a step part 25 in the sectional view.
  • This embodiment can further lower the position of a retainer body 3 by arranging the step part 25 .
  • FIGS. 13 and 14 relate to Embodiment 4 of the present invention, in which FIG. 13 is a sectional view showing a spring retainer and FIG. 14 is a plan view showing the same.
  • the spring retainer 1 D employs a plate-like spring part 5 D having support tongues 23 that are circumferentially arranged at regular intervals.
  • This embodiment can set a spring load by setting the number of the support tongues 23 .
  • FIGS. 15 and 16 relate to Embodiment 5 of the present invention, in which FIG. 15 is a side view showing a spring retainer and FIG. 16 is a plan view showing the same.
  • the spring retainer 1 E employs a plate-like spring part 5 E that is a wave spring.
  • This embodiment can set a spring load by setting waves of the plate-like spring part 5 E.
  • Coil springs applicable to the present invention are not only valve springs but also clutch damper (torsion) springs and the like.
  • the clutch damper (torsion) spring the plate-like spring part (disk spring) having a higher spring constant absorbs impact force (load) that is continuously applied after a coil spring is compressed, thereby preventing the deformation and destruction of the coil spring, as well as the destruction of a seat member (retainer).

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Springs (AREA)
US12/227,345 2006-05-16 2007-05-08 Spring retainer and spring system Expired - Fee Related US7997242B2 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
JP2006-136569 2006-05-16
JP2006136569A JP5063031B2 (ja) 2006-05-16 2006-05-16 スプリング・リテーナ及びスプリング・システム
PCT/JP2007/059495 WO2007132696A1 (ja) 2006-05-16 2007-05-08 スプリング・リテーナ及びスプリング・システム

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US20090235882A1 US20090235882A1 (en) 2009-09-24
US7997242B2 true US7997242B2 (en) 2011-08-16

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US12/227,345 Expired - Fee Related US7997242B2 (en) 2006-05-16 2007-05-08 Spring retainer and spring system

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US (1) US7997242B2 (ja)
EP (1) EP2023003A1 (ja)
JP (1) JP5063031B2 (ja)
CN (1) CN101443576B (ja)
WO (1) WO2007132696A1 (ja)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP5063031B2 (ja) * 2006-05-16 2012-10-31 日本発條株式会社 スプリング・リテーナ及びスプリング・システム
JP5203494B2 (ja) * 2011-10-18 2013-06-05 株式会社東郷製作所 ばねシート部材及びこれを具備するばね組立て体
DE102013009637B4 (de) * 2013-06-06 2020-06-18 Volkswagen Aktiengesellschaft Federunterlage für eine Schraubenfeder

Citations (16)

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Publication number Priority date Publication date Assignee Title
US2582060A (en) * 1947-09-29 1952-01-08 Thompson Prod Inc Valve rotating device
US3068848A (en) * 1960-12-29 1962-12-18 Thompson Ramo Wooldridge Inc Valve rotating mechanism
US3537325A (en) * 1969-01-24 1970-11-03 Gen Motors Corp Valve rotator
US3563218A (en) * 1969-07-07 1971-02-16 Elwood L Havens Valve spring spacer
US3717132A (en) * 1971-11-05 1973-02-20 Gen Motors Corp Valve rotator
US4075987A (en) * 1975-04-23 1978-02-28 Trw Inc. Valve rotator
US4538558A (en) * 1980-12-10 1985-09-03 Trw Inc. Valve rotating device
JPS6141029A (ja) 1984-07-28 1986-02-27 ルーク・ラメレン・ウント・クツプルングスバウ　ゲゼルシヤフト・ミツト・ベシユレンクテル・ハフツング 円形リング形のばね弾性的な皿ばね状の部材
JPS6342810A (ja) 1986-08-08 1988-02-24 佐藤工業株式会社 Ｐｃ鋼材緊張力の自動制御方法
JPH02134430A (ja) 1989-02-01 1990-05-23 Tokushu Hatsujo Kogyo Kk ウェーブ付さらバネ
JPH08319942A (ja) 1995-03-17 1996-12-03 Toyota Autom Loom Works Ltd 両頭斜板式圧縮機
JPH09303455A (ja) 1996-05-07 1997-11-25 Mitsubishi Steel Mfg Co Ltd 円周方向に波を打ったコイルドディスクスプリング
JPH09329155A (ja) 1996-06-10 1997-12-22 Dainatsukusu:Kk 多板式摩擦係合装置のばねプレート
JP2001140980A (ja) 1999-11-16 2001-05-22 Bridgestone Corp ばね構体
JP2001513183A (ja) 1997-12-23 2001-08-28 ヴァレオ 自動車車両トランスミッション用二重減衰フライホイールのための半径方向弾性装置
US20090235882A1 (en) * 2006-05-16 2009-09-24 Nhk Spring Co., Ltd. Spring Retainer and Spring System

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5827509U (ja) * 1981-07-21 1983-02-22 トヨタ自動車株式会社 バルブロ−テ−タ装置
JPS6342810U (ja) * 1986-09-08 1988-03-22
JP3357965B2 (ja) * 1994-10-06 2002-12-16 フジオーゼックス株式会社 内燃機関用バルブローテータ
JPH08180308A (ja) 1994-12-28 1996-07-12 Nec Kansai Ltd コア薄膜磁気ヘッド
DE10103578A1 (de) * 2001-01-26 2002-08-14 Trw Deutschland Gmbh Ventildrehvorrichtung

Patent Citations (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2582060A (en) * 1947-09-29 1952-01-08 Thompson Prod Inc Valve rotating device
US3068848A (en) * 1960-12-29 1962-12-18 Thompson Ramo Wooldridge Inc Valve rotating mechanism
US3537325A (en) * 1969-01-24 1970-11-03 Gen Motors Corp Valve rotator
US3563218A (en) * 1969-07-07 1971-02-16 Elwood L Havens Valve spring spacer
US3717132A (en) * 1971-11-05 1973-02-20 Gen Motors Corp Valve rotator
US4075987A (en) * 1975-04-23 1978-02-28 Trw Inc. Valve rotator
US4538558A (en) * 1980-12-10 1985-09-03 Trw Inc. Valve rotating device
JPS6141029A (ja) 1984-07-28 1986-02-27 ルーク・ラメレン・ウント・クツプルングスバウ　ゲゼルシヤフト・ミツト・ベシユレンクテル・ハフツング 円形リング形のばね弾性的な皿ばね状の部材
JPS6342810A (ja) 1986-08-08 1988-02-24 佐藤工業株式会社 Ｐｃ鋼材緊張力の自動制御方法
JPH02134430A (ja) 1989-02-01 1990-05-23 Tokushu Hatsujo Kogyo Kk ウェーブ付さらバネ
JPH08319942A (ja) 1995-03-17 1996-12-03 Toyota Autom Loom Works Ltd 両頭斜板式圧縮機
JPH09303455A (ja) 1996-05-07 1997-11-25 Mitsubishi Steel Mfg Co Ltd 円周方向に波を打ったコイルドディスクスプリング
JPH09329155A (ja) 1996-06-10 1997-12-22 Dainatsukusu:Kk 多板式摩擦係合装置のばねプレート
JP2001513183A (ja) 1997-12-23 2001-08-28 ヴァレオ 自動車車両トランスミッション用二重減衰フライホイールのための半径方向弾性装置
JP2001140980A (ja) 1999-11-16 2001-05-22 Bridgestone Corp ばね構体
US20090235882A1 (en) * 2006-05-16 2009-09-24 Nhk Spring Co., Ltd. Spring Retainer and Spring System

Also Published As

Publication number Publication date
WO2007132696A1 (ja) 2007-11-22
EP2023003A1 (en) 2009-02-11
JP5063031B2 (ja) 2012-10-31
JP2007309354A (ja) 2007-11-29
US20090235882A1 (en) 2009-09-24
CN101443576A (zh) 2009-05-27
CN101443576B (zh) 2012-01-04

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